US3583376A - Fluid-operated rpm regulator for internal combustion engines - Google Patents

Fluid-operated rpm regulator for internal combustion engines Download PDF

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Publication number
US3583376A
US3583376A US815549A US3583376DA US3583376A US 3583376 A US3583376 A US 3583376A US 815549 A US815549 A US 815549A US 3583376D A US3583376D A US 3583376DA US 3583376 A US3583376 A US 3583376A
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US
United States
Prior art keywords
fluid
pressure
control
amplifier element
output
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US815549A
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English (en)
Inventor
Hiroshi Tonegawa
Hiroshi Isobe
Tadayuki Kawasaki
Kenji Nakayama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Corp
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Diesel Kiki Co Ltd
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Publication date
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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D13/00—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15C—FLUID-CIRCUIT ELEMENTS PREDOMINANTLY USED FOR COMPUTING OR CONTROL PURPOSES
    • F15C1/00—Circuit elements having no moving parts
    • F15C1/002—Circuit elements having no moving parts for controlling engines, turbines, compressors (starting, speed regulation, temperature control or the like)
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
    • Y10T137/2065—Responsive to condition external of system
    • Y10T137/2071—And causing change or correction of sensed condition
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
    • Y10T137/212—System comprising plural fluidic devices or stages
    • Y10T137/2125—Plural power inputs [e.g., parallel inputs]
    • Y10T137/2142—With variable or selectable source of control-input signal

Definitions

  • R.p.m. regulators of the centrifugal governor type which utilize the centrifugal force of rotary weights, include a plurality of rotating and relatively sliding parts and thus may be the source of disturbances. Further, in the low r.p.m.-range the regulating force of these centrifugal governors is often unsatisfactory which may result in an uneven, seesawing" operation of the engine.
  • the r.p.m.-proportionate pressure pulses of a fluid medium are carried by conduits of different lengths to the individual control channels of a fluid logic element and the setting of the fuel control rod is varied in response to the pressure difference between the individual output flows emanating from a fluid amplifier element, the control flows of which are formed, on the one hand, of the output flow of the aforenoted fluid logic element, and, on the other hand, of a flow of constant pressure modulated by the open passage section of an arbitrarily variable throttle in the suction pipe of the internal combustion engine.
  • FIG. I is a diagrammatic illustration of the fluid r.p.m. regulator according to the invention.
  • FIG. 2 is a view of an element taken along arrow A of FIG.
  • FIG. 3 is a perspective view of the flow channels of a fluid logic element
  • FIG. 4 is a perspective view of the flow channels'of a fluid amplifier element
  • FIG. 5 is a diagram illustrating the alternating function between pressure and time in the individual channels of the fluid logic element shown in FIG. 3 and
  • FIG. 6 is a diagram of a characteristic curve of an r.p.m. sensor used according to the invention.
  • FIG. 1 there is shown in broken lines a known pneumatic r.p.m. regulator mounted on a fuel injection pump 1, also shown in broken lines.
  • a fuel control rod 3 which regulates the injected fuel quantities and which is connected at one end with a membrane 4 dividing a chamber 6 from a chamber 7.
  • a spring 8 which opposes the pressure difference between the pressures prevailing in chambers 6 and 7 and which holds the fuel control rod 3 in its required position.
  • the invention provides an arrangement in which the aforedescribed known structure is combined with a fluid logic circuit, now to be described, to effect control of the enginer.p.m. by causing displacement ofthe fuel control rod 3.
  • a circular disc 9 of a pneumatic r.p.m. sensor which, as best shown in FIG. 2, is provided with a plurality ofsmall openings 10 arranged along a common circle.
  • conduit 14 From pickup nozzle 13 there extend two conduits: a conduit 14 and a relatively longer conduit 15.
  • Conduit 14 is attached to the right control channel 17 of a fluid logic element 16, while the conduit 15 is attached to the left control channel 18 thereof.
  • the main flow channel 22 of the fluid logic element 16 communicates with a conduit 21 through which fluid under pressure is introduced from a fluid source (not shown) across the main channel 22 into the control chamber 23 of the fluid logic element 16 (FIG. 3).
  • the control channels 17 and 18 merge into the control chamber 23 from the right and from the left, respectively.
  • the fluid medium arriving from the main channel 22 into the control chamber 23 proceeds, due to the control flow pulses injected into chamber 23 from the control channel 17 or control channel 18, along one of the sidewalls 24 or 25 due to the Coanda-effect.
  • This deflected condition is maintained even after the control signal ceases.
  • the fluid medium either flows in one of the output channels 27, 28 (on-condition) or does not flow (off-condition).
  • the output channel 28 of the fluid logic element 16 is connected through conduit 29 with the control channel 31 of a fluid amplifier element 30, shown in FIG. 4.
  • Fluid medium under pressure is introduced from a fluid source (not shown) through a conduit 34 and through the main flow channel 35 of the amplifier 30 into the control chamber 36 thereof.
  • the main stream arriving from main chan nel 35 is deflected from its course depending on the difference between the fluid quantity arriving from the control channel 31 and that arriving from the control channel 32.
  • the percentual component of these fluid quantities determines the course of flow in such a manner that the main stream enters either the right output channel 38 or the left output channel 39 provided in the lower section of the control channels 31 and 32.
  • the output channels 38 and 39 are, by means of respective conduits 42 and 43, connected with chambers 7 and 6, respectively, which serve to displace the fuel control rod 3.
  • control channel 32 of fluid amplifier element 30 there communicates a conduit 44 in which there is disposed an arbitrarily adjustable throttle 46 for a control flow to set the engine r.p.m., and which is connected with a fluid source of constant pressure, not shown.
  • the control channel 47 disposed parallel with the control channel 31 is, through a conduit 48, also connected with a fluid source of constant pressure (not shown) and constitutes an auxiliary (bias) stream which produces a constant pressure.
  • This auxiliary stream may be replaced by arranging the output channels 38 and 39 unsymmetrically with respect to the axis of the main channel 35.
  • the pump cam shaft 2 together with circular disc 9, rotates at r.p.m.-responsive speeds, while blower nozzle lll emits a continuous stream of fluid directed against disc 9.
  • blower nozzle lll emits a continuous stream of fluid directed against disc 9.
  • pickup nozzle 13 Each time an opening of disc 9 is in a momentary alignment with blower nozzle 11, a fluid pulse is received by pickup nozzle 13.
  • One part of the fluid forming a pulse enters through conduit 14 into the right control channel 17 of the fluid logic element 16 and causes the main stream arriving from the main flow channel 22 to be deflected into the output channel 28.
  • the other part of the fluid forming the same pressure pulse enters through the longer conduit into the left control channel 18 of the fluid logic element 16 with a time lag of T see. and switches the main stream from the output channel 28 to the output channel 27.
  • curve (a) represents the pressure pulses in the control channel 17 as a function of time
  • curve (b) represents the pressure pulses in the control channel m as a function of time and shifted with respect to (a) by T sec.
  • curve (c) represents the pressure pulses in the output channel 28 as related to (a) and (b).
  • the period (on-condition) during which the main stream flows in the output channel 28 is determined by the delay of T sec. of the impulse transmission. This delay, in turn, is a function of the difference in the length of conduits 14, 15 and is independent of the rpm. of disc 9. Since the pulse interval is determined by the r.p.m.
  • the pulse interval is inversely proportionate to the r.p.m. N.
  • lt follows that the average pressure P generated in the output channel 28 of the fluid logic element 16 is, as seen in FIG. 6, proportionate to the r.p.m. N and consequently, the r.p.m. may be determined by the value of P.
  • the pulse signals generated in the output channel 28 of the fluid logic element 16 enter through the conduit 29 into the control channel 311 ofthe fluid amplifier element 30.
  • the pressure signal regulated by throttle 46 and carried by conduit 44 to the control channel 32 of the amplifier 30 and the aforedescribed r.p.m.-responsive pressure signals in control channel 31 are compared with one another.
  • the fuel control rod 3 is shifted into a position of equilibrium with the aid of spring 8 and thus the fuel quantities to be injected are determined.
  • the r.p.m. increases, which results in an increase of the average pressure in the control channel 31 of the fluid amplifier element 30. Consequently, the pressure in the left output channel 39 will be higher than in the right output channel 38. As a result, the pressure in the chamber 6 will increase so that the fuel control rod 3 is displaced towards the left and, consequently, the fuel quantity to be injected is decreased. This, in turn, causes the engine r.p.m. to drop, so that the output and load torques will be equalized and the r.p.m. stabilized anew.
  • the r.p.m. of the engine may be arbitrarily set by changing the flow passage section of the throttle 46, varying thereby the pressure of the fluid medium flowing in control channel 32 of the fluid amplifier element 30.
  • An r.p.m. regulator for shifting a fuel quantity control member associated with an internal combustion engine comprising,
  • B a fluid logic element having at least two control channels and an output channel
  • D means for arbitrarily varying the pressure of a control fluid flow
  • E a fluid amplifier element having at least two control channels and two output channels, said output fluid flow from said fluid logic element being applied to one of said control channels of said fluid amplifier element and said control fluid flow of arbitrarily variable pressure being applied to the other of said control channels of said fluid amplifier element to produce in said output channels of said fluid amplifier element output flows having a pressure difference depending upon the fluid flows in the last named two control channels and F pressure-responsive means receiving said output flows from said fluid amplifier element and being connected to said fuel quantity control member to displace the latter to an extent dependent upon said pressure difference.
  • An r.p.m. regulator as defined in claim 1, wherein said means for generating said fluid pulse signal includes A a disc having at least one opening in its face,
  • B means for rotating said disc at an r.p.m. proportionate to said engine r.p.m.
  • D a pickup nozzle connected to said conduit means and disposed adjacent the other face of said disc to receive a fluid pulse when said opening in said disc is in momentary alignment with said nozzles; consecutive pulses generated during the rotation of said disc constitute said pulse signal.
  • conduit means is formed of two conduits of different lengths leading from said pickup nozzle to said two control channels of said fluid logic element.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Theoretical Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Fuel-Injection Apparatus (AREA)
US815549A 1968-04-15 1969-04-14 Fluid-operated rpm regulator for internal combustion engines Expired - Lifetime US3583376A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2482168 1968-04-15

Publications (1)

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US3583376A true US3583376A (en) 1971-06-08

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US815549A Expired - Lifetime US3583376A (en) 1968-04-15 1969-04-14 Fluid-operated rpm regulator for internal combustion engines

Country Status (4)

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US (1) US3583376A (enrdf_load_stackoverflow)
DE (1) DE1911526A1 (enrdf_load_stackoverflow)
FR (1) FR2006226A1 (enrdf_load_stackoverflow)
GB (1) GB1248626A (enrdf_load_stackoverflow)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2900969A (en) * 1957-12-19 1959-08-25 Holley Carburetor Co Fuel injection system
US3266510A (en) * 1963-09-16 1966-08-16 Sperry Rand Corp Device for forming fluid pulses
US3292648A (en) * 1963-07-05 1966-12-20 Bowles Eng Corp Turbine speed control
US3461892A (en) * 1968-07-25 1969-08-19 Gen Electric Fluid controls particularly for turbine engines
US3463176A (en) * 1965-12-22 1969-08-26 Honeywell Inc Fluidic fuel control system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2900969A (en) * 1957-12-19 1959-08-25 Holley Carburetor Co Fuel injection system
US3292648A (en) * 1963-07-05 1966-12-20 Bowles Eng Corp Turbine speed control
US3266510A (en) * 1963-09-16 1966-08-16 Sperry Rand Corp Device for forming fluid pulses
US3463176A (en) * 1965-12-22 1969-08-26 Honeywell Inc Fluidic fuel control system
US3461892A (en) * 1968-07-25 1969-08-19 Gen Electric Fluid controls particularly for turbine engines

Also Published As

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FR2006226A1 (enrdf_load_stackoverflow) 1969-12-26
GB1248626A (en) 1971-10-06
DE1911526A1 (de) 1969-10-30

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